Combined reciprocating steam engine and turbine



April 19, 1932. H. WACH 1,854,816

COMBINED RECIPROQATING STEAM ENGINE AND TURBINE Filed July 16 I 1926 Patented Apr. 19, 1932 HANS WACH, 0F WESERMUNDE-LEHE, GERMANY COMBINED RECIPROCATING- STEAM ENGINE AND TURBINE Application filed July 16, 1926, Serial No. 122,788, and in Germany March 18, 1926.

This invention relates to power plants consisting essentially of a pair of engines, and has for its general object to provide a novel and practical control apparatus designed to enable both engines to deliver power simultaneously to a shaft for rotating same in one direction, or to enable power to be delivered by one of said engines to said shaft for rotating same in a reverse direction.

In particular, the invention relates to a ship propulsion power plant consisting essentially of a reversible reciprocating steam engine directly connected with a propeller shaft for rotating same in either ahead or astern directions, and a steam turbine deriving its power from the exhaust of the reciprocating engine and adapted to act in conjunction with the latter engine to impart rotation to the propeller shaft in an ahead direction.

According to the invention there is interposed between the turbine engine and the propeller shaft a fluid coupling device to which fluid is adapted to be supplied to couple the turbine engine with said shaft and from which fluid is adapted to be exhausted to disconnect the turbine from said shaft; a

valve is provided to direct or to divert exhaust steam from'the reciprocating engine to and from the turbine; fluid pressure devices are provided for actuating said valve and to open and close a port through which fluid is exhausted from the fluid coupling; a pump is provided for the supply of fluid pressure, and fluid control valves are provided for properly directing the flow of fluid to actuate the steam valve and to eifect supply and exhaust of fluid to and from'the fluid coupling.

The foregoing general arrangement is disclosed in my copending application 122,790. As distinguished from that application, however, the present invention resides in the provision of means whereby a fluid control valve of the apparatus is actuated by the reversing lever or so called telegraph of the reciprocating engine, the object sought to be accomplished in this respect being to assure positive actuation of the fluid control valve to a position to effect a flow of fluid to cut off the supply of steam to the turbine and to disconnect the latter from the propeller shaft when the reversing lever is moved to a reversing position. Also, in this connection, an object of the invention is to provide means automatically operable to actuate the fluid control valve and thus actuate the steam valve to cut ofl the supply of steam to the turbine prior to the reversing lever being moved to its reverse position.

With the foregoing and other objects in view, the invention consists in the novel features of construction, combination and arrangement of parts as will be hereinafter more fully described, illustrated in the accompanying drawings and defined in the appended claims.

In the drawings, wherein like characters of reference denote corresponding parts in the different views:

Fig. 1 is a diagrammatic illustration of a power plant embodying the features-of the invention and showing the parts in ahead driving relation; and

Fig. 2 is a similar view showing the parts in astern driving relation.

Referring to the drawings in detail, a designates a reciprocating steam engine directly connected with a propeller shaft a1, 6 designates a steam turbine releasably connected. with the propeller shaft by means of a fluid coupling device designated generally as c, d designates a conduit connecting the reciprocating engine with the turbine for directing exhaust steam from the former to the latter, d1 designates, generally, a valve interposed in the conduit 03 and inclusive of apiston d2 movable between two positions in one of which, as shown in Fig. 1, it permits flow of steam from the engine a to the turbine b, and in the other of which, as shown in Fig. 2, it diverts steam from the turbine 6 either to the atmosphere or, for example, to a condenser, p designates an oil pump such, for example, as is generally employed for the pressure lubrication of the bearings of an engine, 8 designates a centrifugal governor actuated by the reciprocating engine, 7 designates a valve controlled by said governor, and e designates a combined automatic and manually operable oil flow control valve.

The fluid coupling 0 may be of any suitable known type such that when fluid such as oil is supplied thereto it serves to connect the turbine b with the shaft (11 for driving the latter, and, when fluid is exhausted therefrom, to disconnect the turbine from said shaft. To this end said coupling in its general organization may consist as shown of a fluid containing casing inclusive of a part 01 fixed to a shaft 02, parts 03 loose with respect to said shaft, gear wheels 04; rigid with the loose parts 03 and in mesh with pinions 05 fixed to the turbine shaft, and pinions 06 fixed to the shaft 02 and in mesh with gear wheels 07 fixed to the shaft al. The

shaft 02 has a duct 08 for the supply of fluid to the casing comprised by the parts 01 and 03 and the part 01 of said casing has an. oil

outlet opening 09 adapted to be opened or closed by a valve 010 in the form of reciprocal pin. A casingcll encloses the coupling c and on said casing is mounted a cylinder f having a piston fl therein from which extends a piston rod f2. The valve pin 010 is connected with a ring 012 and the piston rod f2 is inclusive of a forked end engaging said ring whereby the piston fl is effective to actuate the valve pin to open or close the opening 09 in any rotated position of the fluid coupling.

The steam valve d1 likewise may be of any suitable type such that it is adapted to be operated by fluid pressure to a position to direct steam to the turbine b, and is maintained normally; i. e., when not subjected to the influence of fluid pressure, in a position to divert steam from the turbine. To this end said valve is inclusive of a cylinder (Z3 having a piston d4 therein connected by a piston rod d5 with the piston (12 and a coil spring (16 is provided to constantly urge the valve d to a position as shown in Figure 2 in which the supply of steam to the turbine is cut off.

The valve 1- consists essentially of a casing provided with a pair of ports T1 and r2 spaced longitudinally thereof and having reciprocal therein a double piston r3 which in one position denies communication between the ports T1 and T2 and in another position establishes communication between the ports 11 and 12. This piston T3 is adapted to be actuated to its first mentioned position, shown in Fig. 1, by the governor s when the reciprocating engine attains a predetermined speed and is adapted to be moved to its second mentioned position, shown in Fig. 2, by a spring 14 when the reciprocating engine is at rest or is operating at a relatively slow rate of speed.

The valve e consists of a casing inclusive of two separate piston chambers el and 02, in the former of which is a piston 63 and in the latter of which are two double or spaced pairs of pistcns a l and e5, respectively, all connected together by a common piston rod e6 which projects beyond one end of the casing and is provided with a hand grip device 'm, for effecting manual manipulation of said pistons. At each end and at the center of the chamber 02 is a port 07 connected in any suitable manner with an oil collection tank (not shown), While intermediate its ends said chamber e2 is provided with a pair of longitudinally spaced ports 08 and 09 under the control of the double pistons eat, and a series of three longitudinally spaced ports e10, 611 and e12 under the controlof the double pistons e5. The chamber 01 has a port e13 located at its inner end.

A pipe g connects the pump p with the port 1'1 of the valve 1 and from said pipe 9 a branch pipe 1) leads to the various hearings to be lubricated. Also from said pipe q a pipe h leads to the ports a8 and 011 of the valve 6. From the port 12 of the valve 1' a pipe t leads to the port 613 of the cylinder chamber 61. From the port 09 apipe is leads to the cylinder (Z3 at the side of the piston (Z4 therein so that when fluid is supplied through said pipe to said cylinder the piston (Z2 will be moved to the position shown in Fig. 1 to direct steam to the turbine I), while branch ing off from this pipe 70 is a pipe 5 which leads to the duct c in the shaft 0 of the fluid coupling c. From the port 0 21 pipe 0 leads to one end of the cylinder 7, and from the port 01:2 a pipe 02 leads to the other end of the cylinder f.

When the engine a is at rest the valve pistons r3, (Z2, e3, e4, 65, fl and 010 occupy the positions shown in Fig. 2. Consequently, the turbine is disconnected from the shaft a1 and flow of steam to the turbine 7) through the pipe d is prevented. Assuming now that the engine a is started in an ahead direction and is run slowly, it is apparent that oil will be supplied through the ipe g, valve 1' and pipe t to the valve cham er el and through the pipe h to the valve chamber 02 and from said chamber through the pipe 0 to the inner end of the cylinder If new the engine is brought up to a speed to actuate the governor s to in turn actuate the pistons 1'3 of the valve 1', said pistons are moved to the position shown in Fig. 1 and communication between the pipe 9 and t is cut off. At the same time communication is established between the port 7 2 and a port r5 which may lead to the oil tank. Consequently, the inner end of the piston 63 of the valve 6 is relieved of any oil pressure and the pistons (13, c4 and 05 are free to be moved manually by means of the hand grip device m to the position shown in Fig. 1. When this is done the pistons 64 place the pipes 72, and i in communication with one another and the pistons 05 place the port 010 in communication with the middle port 07 leading to the oil tank and establish communication between the ports e11 and e12.

Oil then flows from the pump through the pipes h and n to the outer end of the cylinder f, thereby moving the piston f1 inward to actuate the valve pin 010 to close the outlet opening 09. Since now oil cannot escape from the fluid coupling a the latter becomes filled with oil through the pipes h and 2' and the turbine 12 as a consequence is connected in drivingrelation with the propeller shaft (11 through the fluid coupling. When the fluid coupling becomes filled with a consequent building up of pressure in the pipe '5, oil then flows through the pipe is to the cylinder d3 and actuates the piston d4 to move the piston (Z2 to direct exhaust steam from the engine a to the turbine b. The turbine thereupon begins to operate and to add its power to that of the reciprocating engine for developing torque in the shaft a1.-

lVhen the speed of the engine a isreduced preparatory to reversing same, andduring relatively slow speed reverse or astern operation thereof, the governor is ineffective to maintain the valve 1'3 in the position shown in Fig. 1 and as a consequence said valve is moved by the spring 14 to the position shown in Fig. 2 in which position of said valve com munication is established between the pipes g and t. Oil then flows into the chamber 61 and moves the piston e3 to the position shown in Fig. 2 whereupon the port e8 is blanked, the port e9 is placed in communication with the oil tank through the middle port e7, the ports e10, 611 are placed in communication with one another, and the port e12 is placed in communication with the oil tank through the related end port e7. Consequently, supply of oil to the pipes i and k is denied and the spring then becomes efi'ec- 40 tive to move the valve d2 to the position shown in Fig. 2 to divert steam from the turbine. At the same time oil is supplied through the pipe h, ports e11 and 610 and pipe 0 to the inner end of the cylinder f and the piston fl is moved to actuate the valve 010 to uncover the opening 09, thereby permitting oil to escape from the fluid coupling to disconnect the turbine from the propeller shaft. Thus, upon slowing down of the engine a the turbine is immediately disconnected from the propeller shaft and a subsequent untime- 1 couplingof the turbine with the propeller shaft is rendered impossible because of the pressure of oil against the piston 63 holding the pistons 6-1 and 05 in the position of Fig. 2. When the parts are 'in the position shown in Fig. 1 it is, of course, possible by manipulation of the handle m to actuate the valves 04, 05 to the position shown in-Fig. 2 with the results heretofore set forth.

All of the foregoing is common to my aforesaid copending application 122,790. As heretofore stated, the purpose of the present invention is not only to provide means where bythe valve 0 is positively operated to the position shown in Fig. 2 by the reversing lever of the reciprocating engine when said lever is moved to a reversing position, but is automatically operated to that position prior to the reversing lever actually being moved to its reverse position. To this end the piston rod 06 at its end opposite to the end thereof having the handle m is extended through the casing of the valve 6 and is pivotally connected with one arm 10 of a lever 11 which is intermediately pivoted as at 12 and has its other arm 13 slotted as indicated at '14. The reversing lover of the reciprocating engine is indicated at 15 and rigid with this lever is an arm 16. A rod 17 connects the arm 16 with a pin 18 which is operable in'the slot 14 of the lever 11, the arrangement of said levers and the length of said slot be ing such that when the lever 15 is moved to a reversing position the pin 18 engages an end wall of the slot 14 and positively moves the lever 11 to a position to actuate the pistons 63, c4 and e5 to the position shown in Fig. 2. When the lever 15 is in either stop or forward position the slot- 1 1 provides a lost motion connection between the lever 11 and the arm 16 so that the pistons 63, 04 and e5 may be moved to the position of Fig. l. WVhen the said pistons are in the position shown in Figure 1 movement of the reversing lever to an intermediate or stop position will result in a decrease in the speed of the reciprocating engine. The governor spring 1'? thus will be permitted to act to shift the valve 1' from the position of Figure 1 to the position of Figure 2, whereupon fluid will be directed from the pump p through the ports r and r and the pipe it into the cylinder 6 through the port 6 The fluid acting against the piston 6 thus will shift the pistons e and e to the position shown in Figure 2 with the consequence that the same operation will take place as when the reversing lever is moved to its reverse position.

I claim:

1. In combination, a shaft to be driven, a reciprocating engine connected with said shaft, a turbine, a releasable fluid coupling connection between said turbine and said shaft, a source of fluid pressure, a control lever for the reciprocating engine movable to ahead, stopand reverse positions, a valve for controlling the flow of fluidto and from said fluid coupling, a connection between said control lever and said valve whereby the latter is positively actuated to a position to cause exhaust of fluid from said coupling and to cut off the supply of fluid to said coupling when the control lever is moved from an ahead position to a reverse position, and means operable in response to a reduction in the speed of the reciprocating engine to actuate said'valve to said position independently of movement of the reversing lever to reverse position.

2. In combination, a shaft to be driven, a reciprocating engine connected with said shaft, a turbine, a releasable fluid coupling connection between said turbine and said shaft, a source of fluid pressure, a control lever for the reciprocating engine movable to ahead, stop and reverse positions, a valve for controlling the flow of fluid to and from said fluid coupling, a connection between said control lever and said valve where by the latter is positively actuated to a position to cause exhaust of fluid from said coupling and to cut off the supply of fluid to said coupling when the control lever is moved to a reverse position, said connection providing for lost motion between said control lever and said valve whereby the latter may be moved to a position to direct fluid to said coupling when the control lever is in an ahead position, and means operable in response to a reduction in the speed of the reciprocating engine to actuate said valve to said position independently of movement of the reversing lever to reverse position.

In testimony whereof I have aflixed my signature.

HANS WACH. 

